EP2360438B1 - Fluid turbulator for geothermal probe - Google Patents

Description

The invention relates to a Erdsondenfluidturbolator for a coaxial earth probe according to the preamble of claim 1, which is provided for the exchange of heat between a heat transfer fluid and the ground surrounding the earth probe in which the geothermal probe is arranged in the operating state.

Ground probes can be coaxial or U-shaped. U-shaped geothermal probes have an inflow pipe which leads down into the ground and is connected in a fluid-conducting manner to an outflow pipe at a lower end in a connection region. The heat transfer fluid thus flows down the inflow pipe, merges into the discharge area in the connection area and flows up again in this area. In coaxial ground probes, the inflow pipe is an outer pipe and the exhaust pipe is an inner pipe arranged inside the outer pipe. Outside the inner tube and inside the outer tube is a ring portion forming a heat transfer area. The arrangement of the outer tube to the inner tube is coaxial. The connection region is formed in the case of a coaxial ground probe through an opening of the inner tube, so that heat transfer fluid located in the outer tube or in the annular region can flow here into the inner tube. Such a system is in DE 20 2008 002 048 described.

When passing through the geothermal probe, heat transfer between the heat transfer fluid and the soil takes place. The heat transfer is essentially by convection. Whether heat is emitted or absorbed depends on whether the ground probe is used for a cooling process or a heat process. For this purpose, geological probes are arranged up to 100 m deep in the ground, in individual cases, larger depths are realized.

Typically, multiple ground probes are shared in a geothermal heat loop. Such a Erdsondenwärmekreislauf usually has a Pump and a heat exchanger. By means of the pump, heat transfer fluid is circulated within the ground probe heat circuit. The ground probes can be connected in parallel or in series or in combinations thereof. In the heat exchanger, the obtained temperature difference between the inlet and the derived heat transfer fluid is transferred to a second fluid circuit.

The temperature difference between the heat transfer fluid introduced and discharged into the geothermal probe is referred to below as the temperature gradient. The soil is taken from a heat flow or a heat output.

For geothermal probes less than 100 meters in length or depth, the temperature difference between the heat transfer fluid introduced and the heat transfer fluid removed is typically a few degrees. Typical values are between -2 ° C and 1 ° C and conductance values between 2 ° C and 5 ° C. The temperature difference is relatively low and the heat transfer fluid exiting the geothermal probes is not yet ready to heat e.g. Residential spaces suitable. However, the heat output can be made available with the help of a heat pump.

Usually, a plurality of ground probes are used in a geothermal probe circuit, since the usable temperature difference of a geothermal probe is usually not sufficient to evaporate a heat medium in a second fluid circuit in the heat pump. Especially for ground probes with a length of less than 70 m, the achievable temperature gradient is often insufficient. Furthermore, in some regions, the permitted depth is limited, for example, to protect the groundwater.

For example, is from the DE 30 00 157 A1 , of the DE 20 2008 002 048 , of the EP 2 151 643 A2 from the JP 2004/340/463 It is known that the heat transfer can be improved by placing the heat transfer fluid in a helical rotational movement as it flows through the geothermal probe. For this purpose, helical flow bodies may be provided within the ground probe, which redirects the otherwise laminar incoming heat transfer fluid in a spiral direction. Basically, this measure already leads to an improvement of the heat transfer, however, especially with geothermal probes of less than 100 m, but also in regions where the usable geothermal energy is rather low, the heat yield is still insufficient.

Out JP 2004/3401463 is a geothermal fluid turbulator according to the preamble of claim 1.

This is where the invention begins. It has set itself the task to improve the efficiency of coaxial ground probes and thus the efficiency of coaxial Erdsondenwärmekreisläufen. Furthermore, the invention is to enable the effective use of geothermal probes in regions where laws limit the allowable drilling depth.

According to the invention the object is achieved by a Erdsondenfluidturbulator for a coaxial ground probe with the features of claim 1.

A geothermal fluid turbulator constructed in accordance with the present invention is disposed within a coaxial ground probe in an interior region of an outer tube and is characterized by at least one split ring disc lying in a plane disposed at an angle to an orthogonal plane of a longitudinal axis of the ground probe having a center approximately at the longitudinal axis lies, an inner edge, which serves for fastening the partial annular disc to an inner tube and an outer diameter which is smaller than an inner diameter of the outer tube of the ground probe. The center point and the outer diameter of the partial annular disk are defined as the center point and outer diameter of a closed annular disk, from which the partial annular disk would be produced by cutting out a sector.

By providing a geothermal fluid turbulator, the necessary length of geothermal probe required for the geothermal probe to achieve sufficiently high efficiency can be reduced, and the geothermal probe can also be used in regions where the depth of drilling is geologically or legally limited. The efficiency is due to turbulence of the offside of Erdsondenfluidturbolators achieved approximately laminar flowing heat transfer fluid.

As the heat transfer fluid, water is usually used. Since temperatures can also occur below zero in the cold winter months, frost protection is usually added. Conditionally u.a. Due to the anomaly of the water, its material properties change with temperature. For example, e.g. the density of water is highest at 4 ° C above zero. The change in the material properties of the water leads in geothermal probes, in which no Erdsondenfluidturbolator is arranged, that forms an approximately laminar flow with unequal tempered layers. The unevenly tempered layers are parallel to an outer tube outer surface, wherein in the vicinity of the outer tube inner surface warmer layers are present, which act as insulators of the inner layers. These inner layers therefore absorb little heat. By swirling the heat transfer fluid, this layer formation is canceled, thereby achieving a higher Temparaturgradient.

The increased by the turbulent flow flow resistance is not serious. For example, to penetrate three consecutive probes with 10 to 14 cubic meters of water per hour, a pressure difference of 0.1 bar to 0.3 bar, so that a pump only needs to absorb 100 W to 300 W of power to provide the pressure difference ,

A partial ring disc provides for different flow directions and thereby causing swirling of the heat transfer fluid. Above the ground probe fluid turbulator, the heat transfer fluid flows almost laminar through the outer tube. When hitting a partial annular disk, the heat transfer fluid undergoes a change in direction due to the inclination of the partial annular disc with respect to the orthogonal plane and then flows obliquely through the outer tube along the partial annular disc. If the outer diameter of the partial ring disc is smaller than the inner diameter of the outer tube, the fluid flow is divided into two partial streams: the already described, oblique and an axial between a Outer tube inner surface and the partial annular disc. The division causes additional swirling of the heat transfer fluid.

According to the invention, at least two partial ring disks are arranged adjacent to one another along the longitudinal axis and have angle values with different signs with respect to the orthogonal plane. Such an arrangement resembles a helix when the angular values have approximately equal magnitudes and the partial annular discs are arranged substantially diametrically opposite one another but offset from one another along the longitudinal axis. This geometry promotes the rotary flow.

In addition, the partial ring discs may have one or more recesses through which a further partial flow is achieved. This splits off from the obliquely rotational flow and flows through the recesses, ie approximately parallel to the longitudinal axis, through. The shape of the recesses is essentially arbitrary. However, round, elliptical, kidney-shaped or ring-sectoral recesses are suitable.

Preferably, two adjacent partial annular disks jointly surround the inner pipe by less than 360 ° and three adjacent partial annular disks jointly enclose the inner pipe by more than 360 °. By means of such a geometric arrangement, an additional flow direction is to be achieved: the rotational flow direction is thereby to be additionally divided and, on the one hand, to remain rotational, and, on the other hand, to extend axially between the partial ring disks. An additional mixing is achieved.

Preferably, at least three partial annular disks arranged along the longitudinal axis form a partial disk turbulator. In a particularly advantageous embodiment, this has at least five partial annular discs. Of these, advantageously, at least three partial annular discs have a central angle of about 180 ° and thus prove to be half annular discs. The remaining partial annular discs advantageously have a center angle of about 160 ° to 170 °. They can therefore be made of the partial annular discs with a center angle of about 180 °, characterized in that annular disc sectors of about 10 ° to 30 ° are removed at one of its ends of these part ring discs.

A method for producing a partial annular disk is characterized in that a plate, preferably made of thermoplastic material, which has a round hole in the center, is separated approximately into two equal halves, and from which halves optionally ring sectors are cut off at the end.

Preferably, at least two partial disc turbulators are used, the respective uppermost annular discs are arranged in planes having approximately the same angle values with respect to the orthogonal plane, but with different signs. This ensures that the rotational flow is at least once clockwise and at least once counterclockwise.

Preferably, the earth probe turbulizer additionally includes at least one annular disc having an annular disc surface which preferably extends parallel to the orthogonal plane and has at least one opening in the annular disc surface. The annular disc is attached to the inner tube and surrounds this, whereby an annular surface between the inner tube and the outer tube is largely closed except for the openings of the annular disc. The annular disc thus has a center which lies approximately on the longitudinal axis, an inner diameter which is equal to an outer diameter of the inner tube and an outer diameter which is less than or equal to the inner diameter of the outer tube. In a particularly advantageous design of this washer, its outer diameter and the inner diameter of the outer tube are the same and supports this. The annular disc thus increases the stability of the geothermal probe and limits the axial flow along the outer tube. The shape and number of openings is essentially freely selectable. However, there are three or four round or kidney-shaped openings.

Preferably, two annular discs, which have a distance a along the longitudinal axis and whose openings are rotated around an annular disc angle about the longitudinal axis to each other, form an annular disc pair. This annular disc angle should advantageously be chosen so that in a plan view, the openings of the lower annular disc of the annular disc surface of the upper annular disc are at least partially obscured. Such an arrangement causes the heat transfer fluid does not have to flow purely translational Flußrichtugn between the two annular discs, but also rotationally. This additionally promotes the mixing process.

Preferably, a ground probe on length sections of about 20m to about 25m at least ten Teilscheibeurburbolatoren and at least two annular disc pairs, arranged so that above, between and below the pairs of annular disc Teilscheibenturbolatoren are provided. As a result, a common swirling and mixing of the heat transfer fluid is achieved on these lengths.

The swirling is achieved primarily by the Teilscheibenturbolatoren, in which the heat transfer fluid is divided several times in the three partial streams described above and then mixed again. These processes mainly cause swirling of the heat transfer fluid, which in addition is amplified by rotational direction changes of two along the longitudinal axis adjacent to each other arranged part ring discs. This turbulence process is supported by mixing processes of several pairs of annular disks.

Advantageous embodiments of the invention are each the subject of the dependent claims. It should be noted that the features listed individually in the claims can be combined with each other in any technologically meaningful manner and show further embodiments of the invention. The description, in particular in connection with the figures, additionally characterizes and specifies the invention.

Fig. 1:

eine schematische Darstellung einer Erdsonde mit einem Anschlussdeckel, einem Innenrohr und einem Außenrohr, wobei um das Innenrohr Mittel zur Verwirbelung des Wärmeübertragungsfluids angeordnet sind,

Fig. 2:

eine schematische Darstellung eines Erdsondenwärmekreislaufes mit mehreren Erdsonden, die in Reihe geschaltet sind,

Fig. 3

die Darstellung eines Erdsondenwärmekreislaufes aus Figur 2 in einer Seitenansicht mit in Erdreich angeordneten Erdsonden, die über Leitungen mit einem Wärmetauscher und einer Pumpe verbunden sind, wobei die Erdsonden in Reihe geschaltet sind,

Fig. 4

die schematische Darstellung einer beispielhaften Teilringscheibe,

Fig. 5

die schematische Darstellung eines Teilscheibenturbolators montiert in einer koaxialen Erdsonde und die dadurch verursachten Flussrichtungen des Wärmeübertragungsfluids,

Fig. 6

die schematische Darstellung einer Ringscheibe mit Öffnungen, und

Fig. 7

die schematische Darstellung eines Ringscheibenpaars.

Further advantages and features of the invention will be described in the following description of the figures. In this show:

Fig. 1:

a schematic representation of a ground probe with a connection cover, an inner tube and an outer tube, wherein means are arranged around the inner tube for swirling the heat transfer fluid,

Fig. 2:

a schematic representation of a Erdsondenwärmekreislaufes with multiple ground probes, which are connected in series,

Fig. 3

the representation of a Erdsondenwärmekreislaufes FIG. 2 in a side view with earth probes arranged in soil, which are connected via lines to a heat exchanger and a pump, wherein the ground probes are connected in series,

Fig. 4

the schematic representation of an exemplary partial annular disc,

Fig. 5

the schematic representation of a Partscheubenturbolators mounted in a coaxial earth probe and the resulting flow directions of the heat transfer fluid,

Fig. 6

the schematic representation of an annular disc with openings, and

Fig. 7

the schematic representation of an annular disc pair.

In the following description, both the Particle Turbinator and the entire Earth Probe Fluid Turbulator, it will be assumed that the ground probe is mounted in the vertical direction. If the probe is mounted at an angle, the positions of the individual components may change.

FIG. 1 shows a schematic representation of a ground probe 20. Via an inlet 22 heat transfer fluid is passed into an outer tube 32. The outer tube 32 is a cylindrical member having the inner diameter there as measured on an outer tube inner surface 60. Externally, the outer tube 32 has an outer tube outer surface 62 facing the soil 54. Concentric with the outer tube 32, an inner tube 30 is disposed within the same. It is substantially cylindrical and has an inner tube inner surface 56 on its inwardly facing surface and an inner tube outer surface 58 on its outwardly facing surface. The heat transfer fluid flows within an annular space 64 between inner tube 30 and outer tube 32, the ground probe 20 down. The annulus 64 is bounded horizontally by the outer tube inner surface 60 and the inner tube outer surface 58 and vertically by a connecting portion 68 and the upper end 72 of the ground probe 20. In the region of the upper end 72, an inlet 22 flows into the annular space 64 in a fluid-conducting manner, in the connection region 68 the annular space 64 passes in a fluid-conducting manner into an inner tube interior 66. The inner tube interior 66 is bounded horizontally by the inner tube inner surface 56 and vertically by the connecting region 68 and the drain 40, into which the inner tube space 66 discharges in a fluid-conducting manner.

At the upper end 72, a connection cover 24 is arranged on the outer tube 32. Therein, the inlet 22 is fluid-conductively connected to the annular space 64 and the outlet 40 is fluid-conductively connected to the inner tube interior 66. The connection ceiling 24 forms the interface between the part of the ground probe 20, which is located in the ground 54 and the part that is accessible from the outside. Advantageously, both the inlet 22 and the outlet 40 have means for fastening lines. In a very simple embodiment of the Connection cover 24 placed on the outer tube 32 and sealed. The connection cover 23 shown has a heating coil 34, which is formed from an electrical conductor. Via connection contacts 28, a current can be passed through the heating coil 34 in order to heat the heating coil 34, whereby the connection cover 24 can be welded to the outer tube 32.

The geothermal probe 20 has a length L which varies according to the desired depth, for example between 15m and 25m. The heat transfer fluid absorbs a heat output from the soil 54 during the passage of the annular space 64. The outer tube 32 is advantageously made of a material which has a relatively high heat transfer coefficient. For example, high-density polyethylene, PE-HD for short, can be used. The heat transfer fluid then rises again at a higher temperature inside the inner tube 30.

In a lower end 74 of the ground probe 20, a probe foot 46 is arranged, which tapers conically. This probe foot 46 facilitates penetration of the ground probe 20 into a bore. The probe foot 46 may be connected to the outer tube 32 by a thermal welding process, such as butt dies.

The outer tube 32 usually has a wall thickness wa between 2.5 mm and 5 mm. Preferably, it has a wall thickness wa of 3.2 mm to 3.8 mm. The inner diameter of the outer tube 32 is preferably 100 mm to 180 mm. The inner diameter di of the inner tube 30 is advantageously between 20 mm and 50 mm. The ratio of the diameter di of the inner tube 30 to the diameter da of the outer tube 32 is thus in a range between 0.2 and 0.7, advantageously in a range between 0.25 and 0.35. This ensures that the annular space 64 has a relatively large area and the heat transfer fluid moves therein as slowly as possible. At the same time, it is still ensured that the diameter di of the inner tube 30 is not too small and that no excessively large tube resistance is formed here.

To be able to vent the geothermal probe 20, the geothermal probe 20 according to the invention advantageously has a vent 70. This comprises a vent opening 42, a vent line 36 and a vent valve 38. The vent opening 42 is advantageously arranged at a location of the connection cover 24 located as high as possible. The vent line 36 is connected to the vent opening 42. At the other end of the vent line 36, a vent valve 38 is arranged, for example, a ball valve. For venting the geothermal probe 20, the heat transfer fluid is pressurized and the vent valve 38 is opened.

FIG. 2 shows in plan view a schematic representation of three ground probes 20a, 20b, 20c with lines 52 which are interconnected to realize a Erdsondenwärmekreislaufes 26. Shown is a closed Erdsondenwärmekreislauf 26, in which the heat transfer fluid is first brought by a pump 48 to a higher pressure level. Then, the heat transfer fluid is supplied to a first ground probe 20a. The heat transfer fluid is passed into the annular space 64a. Herein, the heat transfer fluid flows up into the connection region 68, up through the inner tube 30a again and enters the central ground probe 20b. Thereafter, the heat transfer fluid is conducted from the central earth probe 20b into the annulus 64c of the third earth probe 20c. When the heat transfer fluid has passed through all three ground probes 20a, 20b, 20c, it is fed to a heat exchanger 50.

FIG. 3 shows an arrangement of three ground probes 20a, 20b, 20c in series in a side view. The representation is less schematic, in particular, the lines 52 are clearly recognizable as such.

FIG. 4 shows exemplary partial ring discs 76a-76e. These enclose in the inserted state, the inner tube 30 having an outer diameter d1, a center mt and an inner edge 78. The partial annular discs 76 can be connected in any manner with the inner tube 30, for example, welded or glued. The components of the Erdsondenfluidturbulators can be made of the same material, preferably made of thermoplastic Kuststoff, such as the inner tube 30 accordingly be, whereby a slight connection between the annular discs 76 and / or the annular discs 80 is ensured with the inner tube 30.

The outer diameter d1 of the partial annular disc 76 is selected to be slightly smaller than the inner diameter of the outer tube 32. On the one hand this simplifies insertion of the inner tube 30 together with fixed partial annular discs 76 into the outer tube 32, on the other hand the partial annular discs 76 thereby act as spacers between the outer tube 32 and the inner tube 30, or support the two against each other.

FIG. 5 shows a schematic representation of Teilscheibenturbolators 84 in the mounted state. In the illustrated embodiment, this consists of five partial annular discs 76a-76e, whose outer diameter d1 are smaller than the inner diameter of the outer tube 32. The partial annular discs 76a, 76d and 76e are preferably partial annular discs with a center angle of about 180 °, thus forming approximately half annular discs. The partial annular discs 76b and 76c are partial annular discs of less than 180 °. Such is preferably made of a half-ring disc, the end of a ring disk sector is removed. The partial annular discs 76a, 76c and 76e are preferably arranged one above the other in the operating state such that, in a plan view, the partial annular discs 76c and 76e are covered by the partial annular disc 76a. Further, the partial annular discs 76a, 76c and 76e lie in planes which have similar angles with respect to an orthogonal plane to the longitudinal axis 44. Partial ring disks 76b and 76d are arranged in a similar manner to one another and lie opposite the partial annular disks 76a, 76c and 76e with respect to the longitudinal axis. The planes in which the partial ring discs 76b and 76d lie have a similar angle value with respect to the orthogonal plane, but with a different sign than the planes of the partial ring discs 76a, 76c and 76e. So you are inclined in the opposite direction, so to speak. An angle value of approximately 5 ° to 15 ° proves advantageous. The geometry of such a partial disc turbulator 84 is similar to a helix with recesses 88 (between partial annular discs 76b-76c and 76c-76d). As a result, the heat transfer fluid undergoes three flow directions when passing through this Teilstubenturbolators 84. These flow directions and partial flows are through the Arrows in FIG. 5 indicated. A part of the heat transfer fluid passes through the Teilscheibenturbulator 84 in the vertical direction between the outer tube inner surface 60 and the Teilscheibenturbulator 84. A second part is detected by partial ring disc 76a of Teilscheibenturbulators 84 and thereby experiences an oblique, rotational direction. This is additionally split between partial annular discs 76b-76c and 76c-76d into two sub-flows. One part crosses the recesses resulting from the fact that two adjacent partial annular discs 76b-76c, 76c-76d can not be assembled into complete annular discs, but together have a center angle of less than 360 ° and maintain its rotational movement. The remainder flows vertically through the recesses 88, creating additional turbulence.

FIG. 6 shows the schematic representation of an annular disc 80, with an outer diameter d5, an inner diameter d3, a center mr and three openings 82, wherein only one opening may be sufficient. The inner diameter d3 of the annular disc 80 is adapted to the outer diameter of the inner tube 30. As a result, the annular disc 80, similar to the above-described partial ring disc 76, can be fastened to the inner tube 30. However, this attachment preferably takes place in an orthogonal plane of the longitudinal axis 44. The outer diameter d5 of the annular disc 80 is preferably matched to the inner diameter da of the outer tube 32. On the one hand, the annular disc 80 thereby acts as a spacer between the outer tube 32 and the inner tube 30 and on the other hand, the vertical flow of the heat transfer fluid, in particular in the vicinity of the outer tube inner surface 60, thereby interrupted. The heat transfer fluid flows through the three orifice 82, thereby mixing the heat transfer fluid.

FIG. 7 shows a schematic representation of an advantageous combination of two about the longitudinal axis 44 to each other rotated annular discs 80a and 80b, which are mutually, with a distance a in the direction of the longitudinal axis 44, respectively. Such an arrangement forms an annular disk pair 86. By the angle rotated with each other by ß position, at a distance a, an additional mixing of the heat transfer fluid is achieved.

Over a length of about 15m to 25m, a combination of about 10 to 15 Teilscheibenturbulatoren 84 is recommended with at least two annular disc pairs 86. Such a combination has in the uppermost portion of the length of some Ringscheibeurburbolatoren 84, which is followed by an annular disc pair 86. This arrangement is repeated and is completed in the lower part either by a Teilscheibenturbolator 84 or by an annular disk pair 86. It is also advisable to alternate the generated rotational flow direction of the partial disc turbulators 84: if in a plan view, a first Teilsububenturbolator 84 generates a rotational movement of the heat transfer fluid in a clockwise direction, at least a second Partisibenturbolator 84 generate a rotational movement in the counterclockwise direction. Teilscheibeiburbolatoren 84 and / or pairs of annular disks 86 may be arranged in sections or over the entire length of the ground probe 20.

By mixing and swirling the heat transfer fluid through the combination of Teilteiliburburbulatoren 84 and pairs of annular disks 86 takes place an optimal and harmonious energy exchange between soil and heat transfer fluid. As a result, the heat pump achieves highly efficient efficiencies even with small drilling depths of 15m-30m. Obvious advantages of a lower drilling depth include the low purchase and installation costs and the usability of heat pumps in areas with drilling depth limitation.

Of course, the present invention is not limited to the embodiment described above. Thus, the fastening of the annular disks 80 and / or the partial annular disks 76 can alternatively or additionally also take place on the outer pipe inner surface 60 of the outer pipe 32. In the case of an exclusive or partial attachment to the outer tube inner surface 60 of the outer tube 32, the Teilringscheiben 76 and / or the annular discs 80 then complete or partial distances from the inner tube 30 so that between them heat transfer fluid can flow in the axial direction.

Instead of a Teilteilurburbenturbolators 84 can be used to generate the oblique, rotational movement of the heat transfer fluid, a helix, which preferably has holes. The holes then generate the splitting of the rotary flow into a rotational and a vertical portion.

Further, stoppers 84 may be mounted on the part-disk turbulators. These generate additional turbulences of the oblique-rotational flow.

LIST OF REFERENCE NUMBERS

20th

Erdsonde

22nd

Intake

24th

connection cover

26th

Erdsondenwärmekreislauf

28th

connection contact

30th

inner tube

32nd

outer tube

34th

heating coils

36th

vent line

38th

vent valve

40th

procedure

42nd

vent

44th

longitudinal axis

46th

probe base

48th

pump

50th

heat exchangers

52nd

cables

54th

soil

56th

Inner tube inner surface

58th

Inner tube outer surface

60th

Outer tube inner surface

62nd

Outer tube outer surface

64th

annulus

66th

Inner tube space

68th

connecting area

70th

vent

72nd

lower end

74th

lower end

76th

Part washer

78th

inner edge

80th

washer

82nd

opening

84th

Teilscheibenturbolator

86th

Washer pair

88th

recess

Claims (11)

1. A borehole heat exchanger fluid turbolator for a coaxial borehole heat exchanger (20) provided for exchanging heat between a heat transfer fluid and the ground soil surrounding the borehole heat exchanger (1) in which the borehole heat exchanger (20) is disposed in the operating state, wherein at least two adjacent partial annular discs (76, 76a - 76e), which are disposed offset relative to one another along the longitudinal axis (44) and lie in the same plane, which is disposed at an angle to an orthogonal plane of a longitudinal axis (17) of the borehole heat exchanger (20), each comprise

   - a center point mt, which is located approximately on the longitudinal axis (44),

   - an inner edge (41) that serves for attaching the partial annular disc (76, 76a - 76e) to an inner pipe outer surface (58) of an inner pipe (30) of the borehole heat exchanger,

   characterized in that
   the adjacent partial annular discs (76, 76a - 76e)

   - are disposed substantially diametrically opposite to each other,

   - have angle values with different signs with respect to the orthogonal plane, and

   - have an outer diameter d1 that is smaller than an inner diameter d_a of the outer pipe (32) of the borehole heat exchanger (20).
2. The fluid turbolator for a borehole heat exchanger according to claim 2 or 3, characterized in that two adjacent partial annular discs (76) together enclose the inner pipe (30) of the borehole heat exchanger over less than 360°.
3. The fluid turbolator for a borehole heat exchanger according to any one of the above-mentioned claims, characterized in that three adjacent partial annular discs (76, 76a - 76e) together enclose the inner pipe (8) of the borehole heat exchanger over more than 360°.
4. The fluid turbolator for a borehole heat exchanger according to any one of the above-mentioned claims, characterized in that at least one partial annular disc (76, 76a - 76e) has at least one cutout.
5. The fluid turbolator for a borehole heat exchanger according to any one of the above-mentioned claims, characterized in that at least 3 partial annular discs (76, 76a - 76e) disposed one below the other form a partial disc turbolator (84).
6. The fluid turbolator for a borehole heat exchanger according to claim 5, characterized in that at least 2 partial disc turbolators (84) are used, whose uppermost partial annular discs (76a) lie in planes that have approximately the same angle values with different signs with respect to the orthogonal plane.
7. The fluid turbolator for a borehole heat exchanger according to any one of the above-mentioned claims, characterized in that at least one stopper is attached to a surface of at least one partial annular disc (76, 76a - 76e).
8. The fluid turbolator for a borehole heat exchanger according to any one of the above-mentioned claims, characterized in that the fluid turbolator for a borehole heat exchanger additionally includes at least one annular disc (80), comprising

   - an annular-disc surface that preferably extends parallel to the orthogonal plane,

   - at least one opening (82) in the annular-disc surface,

   - a center point mr, which is located approximately on the longitudinal axis (44),

   - an inner diameter d3, which is equal to an outer diameter d₄ of the inner pipe (30) of the borehole heat exchanger,

   - an outer diameter d5 that is smaller than or equal to the inner diameter da of the outer pipe (32) of the borehole heat exchanger.
9. The fluid turbolator for borehole heat exchanger according to claim 8, characterized in that the outer diameter d5 of the annular disc is equal to the inner diameter da of the outer pipe (32) of the borehole heat exchanger.
10. The fluid turbolator for a borehole heat exchanger according to claim 8 or 9, characterized in that two annular discs (80), which have a distance a from each other along the longitudinal axis (44) and whose openings (82) are disposed in a manner rotated relative to each other by an annular-disc angle β about the longitudinal axis (44), form an annular-disc pair (86).
11. The fluid turbolator for a borehole heat exchanger according to claim 10, characterized in that a borehole heat exchanger (1) comprises at least 10 partial disc turbolators (84) and at least 2 annular-disc pairs (86) over lengths of approximately 20 m to approximately 25 m, disposed in such a way that partial disc turbolators (84) are provided above, between and below the annular-disc pairs (86).

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